|Publication number||US7909601 B2|
|Application number||US 11/338,312|
|Publication date||Mar 22, 2011|
|Priority date||Jan 24, 2006|
|Also published as||CN101360951A, US20070172783, WO2007087042A1|
|Publication number||11338312, 338312, US 7909601 B2, US 7909601B2, US-B2-7909601, US7909601 B2, US7909601B2|
|Inventors||George Stephens, David Spicer, Kurt Edward Kraus|
|Original Assignee||Exxonmobil Chemical Patents Inc.|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (110), Referenced by (8), Classifications (20), Legal Events (2)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This invention relates to an improvement in a burner such as those employed in high temperature furnaces in the steam cracking of hydrocarbons. More particularly, it relates to an improved dual fuel (gas/non-gaseous) burner capable of providing good combustion efficiency, stable combustion and low soot production.
Steam cracking has long been used to crack various hydrocarbon feedstocks into olefins, preferably light olefins such as ethylene, propylene, and butenes. Conventional steam cracking utilizes a furnace which has two main sections: a convection section and a radiant section. The hydrocarbon feedstock typically enters the convection section of the furnace as a liquid or gas wherein it is typically heated and vaporized by indirect contact with hot flue gas from the radiant section and by direct contact with steam. The vaporized feedstock and steam mixture is then introduced into the radiant section where the cracking takes place.
Conventional steam cracking systems have been effective for cracking high-quality feedstock which contains a large fraction of light volatile hydrocarbons, such as naphtha. However, steam cracking economics sometimes favor cracking lower cost feedstocks containing resids such as, atmospheric resid and crude oil. Crude oil and atmospheric resid often contain high molecular weight, non-volatile components with boiling points in excess of 590° C. (1100° F.). Cracking heavier feeds produces large amounts of tar. There are other feeds, such as gas-oils and vacuum gas oils, that produce large amounts of tar and are also problematic for conventional steam cracking systems.
In conventional chemical manufacturing processes, steam cracker tar is typically an undesired side product. When large volumes of low value steam cracker tar are produced, the refiner is placed in the position of blending the tar into heavy fuels or other low value products. Alternatively, steam cracker tar can be used as a fuel within the refinery; however, its physical and chemical properties make it extremely difficult to burn cleanly and efficiently.
Burners used in large industrial furnaces typically use either liquid or gaseous fuel. Liquid fuel burners typically mix the fuel with steam prior to combustion to atomize the fuel to enable more complete combustion, and mix combustion air with the fuel at the zone of combustion.
Gas fired burners can be classified as either premix or raw gas, depending on the method used to combine the air and fuel. They also differ in configuration and the type of burner tip used.
Raw gas burners inject fuel directly into the air stream, such that the mixing of fuel and air occurs simultaneously with combustion. Since airflow does not change appreciably with fuel flow, the air register settings of natural draft burners must be changed after firing rate changes. Therefore, frequent adjustment may be necessary, as explained in detail in U.S. Pat. No. 4,257,763, which patent is incorporated herein by reference. In addition, many raw gas burners produce luminous flames.
Premix burners mix the fuel with some or all of the combustion air prior to combustion. Since premixing is accomplished by using the energy present in the fuel stream, airflow is largely proportional to fuel flow. As a result, therefore, less frequent adjustment is required. Premixing the fuel and air also facilitates the achievement of the desired flame characteristics. Due to these properties, premix burners are often compatible with various steam cracking furnace configurations.
Floor-fired premix burners are used in many steam crackers and steam reformers primarily because of their ability to produce a relatively uniform heat distribution profile in the tall radiant sections of these furnaces. Flames are non-luminous, permitting tube metal temperatures to be readily monitored. As such, the premix burner is the burner of choice for such furnaces. Premix burners can also be designed for special heat distribution profiles or flame shapes required in other types of furnaces.
The majority of recent burner designs for gas-fired industrial furnaces are based on the use of multiple fuel jets in a single burner. Such burners may employ fuel staging, flue-gas recirculation, or a combination of both. Certain burners may have as many as 8-12 fuel nozzles in a single burner. The large number of fuel nozzles requires the use of very small diameter nozzles. In addition, the fuel nozzles of such burners are generally exposed to the high temperature flue-gas in the firebox.
Because of the interest in recent years to reduce the emission of pollutants and improve the efficiency of burners used in large furnaces and boilers, significant improvements have been made in burner design. One technique for reducing emissions that has become widely accepted in industry is known as staging. With staging, the primary flame zone is deficient in either air (fuel-rich) or fuel (fuel-lean). The balance of the air or fuel is injected into the burner in a secondary flame zone or elsewhere in the combustion chamber. Combustion staging results in reducing peak temperatures in the primary flame zone and has been found to alter combustion speed in a way that reduces NOx. However this must be balanced with the fact that radiant heat transfer decreases with reduced flame temperature, while CO emissions, an indication of incomplete combustion, may actually increase.
In the context of premix burners, the term primary air refers to the air premixed with the fuel; secondary, and in some cases tertiary, air refers to the balance of the air required for proper combustion. In raw gas burners, primary air is the air that is more closely associated with the fuel; secondary and tertiary air is more remotely associated with the fuel. The upper limit of flammability refers to the mixture containing the maximum fuel concentration (fuel-rich) through which a flame can propagate.
U.S. Pat. No. 2,813,578, the contents of which are incorporated by reference in their entirety, proposes a heavy liquid fuel burner, which mixes the fuel with steam for inspiration prior to combustion. The inspirating effect of the fuel and steam draws hot furnace gases into a duct and into the burner block to aid in heating the burner block and the fuel and steam passing through a bore in the block. This arrangement is said to be being effective to vaporize liquid fuel and reduce coke deposits on the burner block and also to prevent any dripping of the oil.
U.S. Pat. No. 2,918,117 proposes a heavy liquid fuel burner, which includes a venturi to draw products of combustion into the primary air to heat the incoming air stream to therefore completely vaporize the fuel.
U.S. Pat. No. 4,230,445, the contents of which are incorporated by reference in their entirety, proposes a fluid fuel burner that reduces NOx emissions by supplying a flue gas/air mixture through several passages. Flue gas is drawn from the combustion chamber through the use of a blower.
U.S. Pat. No. 4,575,332, the contents of which are incorporated by reference in their entirety, proposes a burner having both oil and gas burner lances, in which NOx emissions are reduced by discontinuously mixing combustion air into the oil or gas flame to decelerate combustion and lower the temperature of the flame.
U.S. Pat. No. 4,629,413 proposes a low NOx premix burner and discusses the advantages of premix burners and methods to reduce NOx emissions. The premix burner of U.S. Pat. No. 4,629,413 is said to lower NOx emissions by delaying the mixing of secondary air with the flame and allowing some cooled flue gas to recirculate with the secondary air. The contents of U.S. Pat. No. 4,629,413 are incorporated by reference in their entirety.
U.S. Pat. No. 5,092,761 proposes a method and apparatus for reducing NOx emissions from premix burners by recirculating flue gas. Flue gas is drawn from the furnace through recycle ducts by the inspirating effect of fuel gas and combustion air passing through a venturi portion of a burner tube. Airflow into the primary air chamber is controlled by dampers and, if the dampers are partially closed, the reduction in pressure in the chamber allows flue gas to be drawn from the furnace through the recycle ducts and into the primary air chamber. The flue gas then mixes with combustion air in the primary air chamber prior to combustion to dilute the concentration of oxygen in the combustion air, which lowers flame temperature and thereby reduces NOx emissions. The flue gas recirculating system may be retrofitted into existing burners or may be incorporated in new low NOx burners. The entire contents of U.S. Pat. No. 5,092,761 are incorporated herein by reference.
U.S. Pat. No. 5,516,279 proposes an oxy-fuel burner system for alternately or simultaneously burning gaseous and liquid fuels. Proposed therein is the use of a gaseous fuel jet emanating from an oxy-fuel burner that is either undershot by an oxygen lance or is sandwiched between oxidant jets produced by two subsidiary oxidant jets which are preferably formed of oxygen. An actuable second fuel nozzle is proposed for producing a second fuel jet composed of liquid fuel which is angled toward the oxidant jet at an angle of less than 200. When liquid fuel is to be used, it is proposed that the gaseous fuel be turned off and the liquid fuel turned on and vice-versa or both can operate simultaneously where the oxidant supplies oxygen to both fuel streams.
U.S. Pat. No. 6,877,980, the contents of which are hereby incorporated by reference for all that they disclose, proposes a burner for use in furnaces, such as in steam cracking. The burner includes a primary air chamber; a burner tube having an upstream end, a downstream end and a venturi intermediate said upstream and downstream ends, said venturi including a throat portion having substantially constant internal cross-sectional dimensions such that the ratio of the length to maximum internal cross-sectional dimension of said throat portion is at least 3, a burner tip mounted on the downstream end of said burner tube adjacent a first opening in the furnace, so that combustion of the fuel takes place downstream of said burner tip and a fuel orifice located adjacent the upstream end of said burner tube, for introducing fuel into said burner tube.
Notwithstanding the widespread use of single fuel burners, there has been considerable interest in dual fuel burners which use both gas and liquid fuels simultaneously. Various benefits can be obtained through the use of a dual fuel implementation. For example, these burners can be designed, in many cases, to permit either dual fuel combustion or gas only combustion and thus provide flexibility in fuel selection. The conventional wisdom when designing dual fuel burners is to supply a large amount of air to the liquid fuel flame in an effort to achieve efficient combustion with minimal carbon and soot production. It is also typical for these burners to have a completely separate gas and liquid flame because it is thought that the gaseous flame has such a high combustion rate that it will use up most of the oxygen and thus deprive the liquid fuel of the oxygen that it needs to provide efficient combustion.
As may be appreciated, one possible fuel for use in a dual fuel burner is steamcracker tar. Steamcracker tar typically has a very low ash content which helps to minimize the amount of particulates ultimately emitted from the flame. However, there are concerns when steamcracker tar is burned in a conventional dual fuel burner particularly in an overly air-rich environment.
First, if too much air is used, the combustion temperature in the burner can become too low. In this event, the combustion efficiency decreases and the carbon production of the burner will increase. Second, flame stability can become an issue in that the flame may oscillate between complete or nearly complete combustion to severely incomplete combustion. As a result of incomplete combustion, a significant amount of soot will be produced by the burner.
Despite these advances in the art, what is needed is a dual fired gaseous/non-gaseous burner which permits flexibility in fuel selection and which has good combustion efficiency, has a stable flame and has low soot production characteristics.
In one aspect, provided is a dual fuel gas/non-gaseous burner and which may be used in furnaces such as those employed in steam cracking. The burner includes a primary air chamber for supplying a first portion of air; a burner tube having an upstream end and a downstream end; a burner tip mounted on the downstream end of the burner tube adjacent a first opening in the furnace, so that combustion of the fuel takes place downstream of the burner tip producing a gaseous fuel flame; at least one air port in fluid communication with a secondary air chamber for supplying a second portion of air; and at least one non-gaseous fuel gun for supplying atomized non-gaseous fuel, the at least one non-gaseous fuel gun having at least one fuel discharge orifice, the at least one non-gaseous fuel gun positioned within the at least one air port.
In another aspect, provided is a method for combusting an atomized non-gaseous fuel, a gaseous fuel and air within a burner of a furnace, comprising the steps of: combining the gaseous fuel and a first portion of combustion air at a predetermined location; combusting the gaseous fuel at a first combustion point downstream of the predetermined location to produce a gaseous fuel flame; discharging a second portion of combustion air into the furnace through at least one air port; providing the atomized non-gaseous fuel to at least one fuel discharge orifice, the at least one fuel discharge orifice positioned within the at least one air port; and combusting the non-gaseous fuel at a second combustion point.
The burners disclosed herein provide a burner arrangement with good flame stability, low soot production and good combustion efficiency.
The several features of the burners disclosed herein will be apparent from the detailed description taken with reference to accompanying drawings.
The invention is further explained in the description that follows with reference to the drawings illustrating, by way of non-limiting examples, various embodiments of the invention wherein:
Although the present invention is described in terms of a burner for use in connection with a furnace or an industrial furnace, it will be apparent to one of skill in the art that the teachings of the present invention also have applicability to other process components such as, for example, boilers. Thus, the term furnace herein shall be understood to mean furnaces, boilers and other applicable process components.
As shown in
In addition to the gas fuel supplied through gas fuel spud 24 and combusted at burner tip 20, non-gaseous fuel may also be combusted by burner 10. Further to this capability, one or more non-gaseous fuel guns 200 are positioned within the staged air ports 30 of burner 10. Suitable sources of non-gaseous fuel include, by way of example, but not of limitation, steamcracker tar, catalytic cracker bottoms, vacuum resids, atmospheric resids, deasphalted oils, resins, coker oils, heavy gas oils, shale oils, tar sands or syncrude derived from tar sands, distillation resids, coal oils, asphaltenes and other heavy petroleum fractions. Other fuels which may be of interest include pyrolysis fuel oil (PFO), virgin naphthas, cat-naphtha, steam-cracked naphtha, and pentane.
As will become more apparent, the burner of the present invention may operate using only gaseous fuel or using both gaseous and non-gaseous fuel simultaneously. When operating in a dual fuel (gaseous/non-gaseous) mode, the burner may be designed and set so that combustion of the non-gaseous fuel produces from about 0 to about 50% of the overall burner's heat release. Further, the burner may be designed and set so that combustion of the non-gaseous fuel produces from about 0 to about 37% of the burner's heat release. Still yet further, the burner may be designed and set so that combustion of the non-gaseous fuel produces from about 0 to about 25% of the burner's heat release. When operating in a dual fuel mode wherein combustion of the non-gaseous fuel produces about 50% of the overall burner's heat release, it has been found that temperatures at the burner floor may approach levels that are undesirably high.
Referring again to
As may be appreciated, the high flow of staged air flowing through staged air ports 30 creates a super-stoichiometric oxygen environment for combustion. In other words, the air flow in the air ports supplies much more air than needed for complete combustion of the non-gaseous fuel. Further, the high temperatures within the radiant box will also help completely vaporize the non-gaseous fuel to achieve more efficient combustion. As a result, the problems typically associated with incomplete combustion are eliminated.
It is desirable to configure the at least one non-gaseous discharge orifice of the at least one non-gaseous fuel gun so that the non-gaseous fuel is injected toward the gaseous fuel flame prior to combustion. While not impinging upon the flow itself, the radiant heat from the gaseous flame will have the effect of stabilizing the non-gaseous flame, which will also tend to reduce soot production. Additionally, the high temperatures emanating from the gaseous flame of burner 10 will also serve to vaporize the non-gaseous fuel, to achieve more efficient combustion. As a result, the problems typically associated with incomplete combustion are minimized or even eliminated.
Various embodiments of the present invention are possible. In one embodiment, the fuel discharge orifice 204 of non-gaseous fuel discharge tip section 210 may be a single orifice, positioned so as to be parallel with the centerline of the gas flame and the extended centerline of the burner tube 12. In an alternate embodiment, the at least one fuel discharge orifice 204 is directed at an angle θ from a line parallel with the centerline of the burner tube, with reference to the burner floor 14, toward the gas flame (an angle less than 90°), in order to stabilize the non-gaseous flame. For example, the at least one fuel discharge orifice 204 may be directed at an angle of between about 5 and about 10 degrees from a line parallel with the centerline of the burner tube, with reference to the burner floor 14. In particular, as shown in
In another embodiment, the tips of fuel guns 204 are centered within air ports 30, although it is also possible to offset the fuel guns 200 from the center of air ports 30, if desired. In still another embodiment, all air ports 30 contain a fuel gun 200, although it is possible to implement the present invention with only a subset of air ports 30 including a fuel gun 200, as shown in
Referring again to
Optionally, mixing may be promoted by providing two or more primary air channels 37 and 38 protruding into the FGR duct 76. The channels 37 and 38 are conic-section, cylindrical, or squared and a gap between each channel 37 and 38 produces a turbulence zone in the FGR duct 76 where good flue gas/air mixing occurs.
The geometry of channels 37 and 38 is designed to promote mixing by increasing air momentum into the FGR duct 76. The velocity of the air is optimized by reducing the total flow area of the primary air channels 37 and 38 to a level that still permits sufficient primary air to be available for combustion, as those skilled in the art are capable of determining through routine trials.
Mixing may be further enhanced by providing a plate member 83 at the lower end of the inner wall of the FGR duct 76. The plate member 83 extends into the primary air chamber 26. Flow eddies are created by flow around the plate of the mixture of flue gas and air. The flow eddies provide further mixing of the flue gas and air. The plate member 83 also makes the FGR duct 76 effectively longer, and a longer FGR duct also promotes better mixing.
The improvement in the amount of mixing between the recirculated flue gas and the primary air caused by the channels 37 and 38 and the plate member 83 results in a higher capacity of the burner to inspirate flue gas recirculation and a more homogeneous mixture inside the venturi portion 19. Higher flue gas recirculation reduces overall flame temperature by providing a heat sink for the energy released from combustion. Better mixing in the venturi portion 19 tends to reduce the hot-spots that occur as a result of localized high oxygen regions.
Unmixed low temperature ambient air (primary air), is introduced through angled channels 37 and 38, each having a first end comprising an orifice 37 a and 38 a, controlled by damper 37 b, and a second end comprising an orifice which communicates with FGR duct 76. The ambient air so introduced is mixed directly with the recirculated flue gas in FGR duct 76. The primary air is drawn through channels 37 and 38, by the inspirating effect of the gas fuel passing through the fuel orifice, which may be contained within gas spud 24. The ambient air may be fresh air as discussed above.
Advantageously, a mixture of from about 20% to about 80% flue gas and from about 20% to about 80% ambient air should be drawn through FGR duct 76. It is particularly preferred that a mixture of about 50% flue gas and about 50% ambient air be employed.
In operation, fuel orifice 11, which may be located within gas spud 24, discharges gas fuel into burner tube 12, where it mixes with primary air, recirculated flue gas or mixtures thereof. The mixture of fuel, recirculated flue-gas and primary air then discharges from burner tip 20. The mixture in the venturi portion 19 of burner tube 12 is maintained below the fuel-rich flammability limit; i.e. there is insufficient air in the venturi to support combustion. Secondary air is added to provide the remainder of the air required for combustion.
The cross-section of FGR duct 76 may be designed so as to be substantially rectangular, typically with its minor dimension ranging from 30% to 100% of its major dimension. Conveniently, the cross sectional area of FGR duct 76 ranges from about 5 square inches to about 12 square inches/million (MM) Btu/hr burner capacity and, in a practical embodiment, from 34 square inches to 60 square inches. In this way the FGR duct 76 can accommodate a mass flow rate of at least 100 pounds per hour per MM Btu/hr burner capacity, preferably at least 130 pounds per hour per MM Btu/hr burner capacity, and still more preferably at least 200 pounds per hour per MM Btu/hr burner capacity. Moreover, FGR ratios of greater than 10% and up to 15% or even up to 20% can be achieved.
Advantageously, the burner disclosed herein may be operated at about 2% oxygen in the flue gas (about 10 to about 12% excess air). In addition to the use of flue gas as a diluent, another technique to achieve lower flame temperature through dilution is by the use of steam injection. Steam can be injected in the primary air or the secondary air chamber. Steam may be injected through one or more steam injection tubes 15, as shown in
Although the invention has been described with reference to particular means, materials and embodiments, it is to be understood that the invention is not limited to the particulars disclosed and extends to all equivalents within the scope of the claims.
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|U.S. Classification||431/278, 431/162, 431/174, 431/175, 431/4, 431/177, 431/9, 431/8, 431/2|
|Cooperative Classification||F23C9/08, F23D11/102, F23D11/446, F23D17/002, F23C6/047|
|European Classification||F23D11/44B3, F23D17/00B, F23C9/08, F23D11/10A1, F23C6/04B1|
|Jan 24, 2006||AS||Assignment|
Owner name: EXXONMOBIL CHEMICAL PATENTS INC., TEXAS
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:STEPHENS, GEORGE;SPICER, DAVID;KRAUS, KURT;REEL/FRAME:017489/0547
Effective date: 20060124
|Aug 25, 2014||FPAY||Fee payment|
Year of fee payment: 4